CN1502799A - Stroke changeable engine - Google Patents
Stroke changeable engine Download PDFInfo
- Publication number
- CN1502799A CN1502799A CNA2003101152272A CN200310115227A CN1502799A CN 1502799 A CN1502799 A CN 1502799A CN A2003101152272 A CNA2003101152272 A CN A2003101152272A CN 200310115227 A CN200310115227 A CN 200310115227A CN 1502799 A CN1502799 A CN 1502799A
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- China
- Prior art keywords
- stroke
- running shaft
- connecting rod
- rod
- bent axle
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
Abstract
A variable stroke engine includes: a connecting rod connected at one end to a piston through a piston pin; a subsidiary arm turnably connected at one end to the other end of the connecting rod and connected to a crankshaft through a crankpin; and a control rod connected at one end to the subsidiary arm at a position displaced from a connection position of the connecting rod; a support position of the other end of the control rod being capable of being displaced in a plane perpendicular to an axis of the crankshaft. In the variable stroke engine, a switchover means switches over: a state in which a high expansion stroke is provided such that the stroke of the piston in an expansion stroke is larger than that in a compression stroke when an engine load is high; and a state in which a constant compression ratio is provided when the engine load is low. Thus, a reduction in fuel consumption is achieved irrespective of the level of an engine load, while putting a high value on a reduction in fuel consumption in a state in which the engine load is low.
Description
Technical field
The present invention relates to a kind of variable stroke engine, this variable stroke engine comprises: connecting rod, and an end of this connecting rod links to each other with piston by wrist pin; Sub-arm, an end of this sub-arm is connected rotationally with the other end of connecting rod, and this sub-arm links to each other with bent axle by crank pin; And controlling rod, an end of this controlling rod is connected with the position of sub-arm at the link position that leaves connecting rod, and the bearing position of the other end of this controlling rod can move in perpendicular to the plane of crankshaft center line.
Background technique
Such motor is for example known by Japanese patent application No.9-228858, U.S. Patent No. 4517931 etc., wherein, the stroke of piston in expansion stroke is greater than the stroke in compression stroke, therefore, under the identical situation of the amount of inhaled air-fuel mixture, realize bigger expansion work, thereby improve the circuit thermal efficiency.
In above-mentioned common known engine, no matter engine loading how, the stroke of piston in expansion stroke be all greater than the stroke in compression stroke, thereby improve the circuit thermal efficiency.But, when engine loading is low, wish that motor can carry out work under the situation that reduces fuel consumption greatly.
Summary of the invention
In view of the foregoing propose the present invention, the purpose of this invention is to provide a kind of variable stroke engine, wherein,, make fuel consumption that bigger reduction be arranged when motor is in when hanging down load condition simultaneously no matter the load level of motor how, can reduce fuel consumption.
To achieve these goals, the invention provides a kind of variable stroke engine, it comprises: connecting rod, and an end of this connecting rod links to each other with piston by wrist pin; Sub-arm, an end of this sub-arm is connected rotationally with the other end of connecting rod, and this sub-arm links to each other with bent axle by crank pin; And controlling rod, an end of this controlling rod is connected with the position of sub-arm at the link position that leaves connecting rod; The bearing position of the other end of this controlling rod can move in perpendicular to the plane of described crankshaft center line, wherein, this motor also comprises conversion equipment, this conversion equipment can changed between the following state: provide the state of Higher expansion ratio when engine loading is higher, thereby the stroke of piston in expansion stroke is greater than the stroke in compression stroke; And the state that constant compression pressure is provided when engine loading is low.
By this structure of the present invention, when engine loading is higher, higher expansion ratio is provided and when engine loading is low, provides constant compression pressure.Therefore, no matter the load of motor how, can reduce fuel consumption, when being in, motor can further reduce fuel consumption when hanging down load condition simultaneously.
Description of drawings
Fig. 1 is the front view of the motor of first embodiment of the invention.
Fig. 2 cuts open the sectional view of getting along the line 2-2 among Fig. 1.
Fig. 3 cuts open the sectional view of getting along the line 3-3 among Fig. 2.
Fig. 4 cuts open the sectional view of getting along the line 4-4 among Fig. 3.
Fig. 5 is the enlarged view of the major component of Fig. 2.
Fig. 6 cuts open the amplification view of getting along the line 6-6 among Fig. 5.
Fig. 7 cuts open the amplification view of getting along the line 7-7 among Fig. 5.
Fig. 8 cuts open the sectional view of getting along the line 8-8 among Fig. 5.
Fig. 9 is the planimetric map that cuts open the partial cutaway of getting when motor is in low load condition along the line 9-9 among Fig. 1.
Figure 10 is the view that is similar to Fig. 9, and still the motor shown in is in high load condition.
Figure 11 is the plotted curve of the relation between the decrease of expression load of motor and fuel consumption.
Figure 12 is the front view of the motor of second embodiment of the invention.
Figure 13 cuts open the sectional view of getting along the line 13-13 among Figure 12.
Figure 14 cuts open the sectional view of getting along the line 14-14 among Figure 13.
Figure 15 cuts open the sectional view of getting along the line 15-15 among Figure 13.
Figure 16 is the enlarged view of the major component of Figure 13.
Figure 17 cuts open the amplification view of getting along the line 17-17 among Figure 16.
Figure 18 cuts open the amplification view of getting along the line 18-18 among Figure 16 when motor is in high load condition.
Figure 19 cuts open the amplification view of getting along the line 19-19 among Figure 16 when motor is in high load condition.
Figure 20 is the view that is similar to Figure 18, and still the motor shown in is in low load condition.
Figure 21 is the view that is similar to Figure 19, and still the motor shown in is in low load condition.
Figure 22 is the planimetric map that cuts open the partial cutaway of getting when motor is in low load condition along the line 22-22 among Figure 12.
Figure 23 is the view that is similar to Figure 22, and still the motor shown in is in high load condition.
Embodiment
At first referring to figs. 1 to 3, motor is the air cooling single-cylinder engine that for example is used for working machine etc., and it has engine block 21, and this engine block comprises: crank box 22; Cylinder block 23, this cylinder block 23 is inclined upwardly a little, and protrudes from a side of crank box 22; And cylinder head 24, this cylinder head 24 is connected with the head of cylinder block 23.A large amount of air cooling fin 23a and 24a are arranged on the outer surface of cylinder block 23 and cylinder head 24.Crank box 22 is installed on the cylinder head of any working machine by the installation surface 22a on its bottom surface.
The other end 27b that flywheel 32 is fixed on bent axle 27 goes up and is positioned at the outside of this casing 25.Be used for providing the cooling fan 33 of cooling air to be fixed on this flywheel 32 to the each several part of engine block 21.Kick-starter 34 is arranged in the outside of cooling fan 33.
Cylinder-bore 39 is formed in the cylinder block 23.Piston 38 is loaded in this cylinder-bore 39 slidably.Firing chamber 40 is formed between this cylinder block 23 and the cylinder head 24, and like this, the top surface of piston 38 is facing to firing chamber 40.
The suction port 41 and the exhaust port 42 that can lead to firing chamber 40 are formed in the cylinder head 24.Aspirating valves 43 is used to make suction port 41 and firing chamber 40 to interconnect and disconnects, and outlet valve 44 is used to make exhaust port 42 and firing chamber 40 to interconnect and disconnects, and this Aspirating valves 43 and outlet valve 44 are arranged in the cylinder head 24 can open with closable mode.Spark plug 45 is installed on the cylinder head 24 by screw thread, and its electrode is facing to firing chamber 40 simultaneously.
Carburetor 35 links to each other with the top of cylinder head 24.The downstream of the air intake passage 41 of Carburetor 35 is communicated with suction port 41.The sucking pipe 47 that leads to the upstream extremity of air intake passage 46 links to each other with Carburetor 35, also links to each other with unshowned air cleaner.The outlet pipe 48 that leads to exhaust port 42 links to each other with the top of cylinder head 24, also links to each other with muffler 49.And, fuel tank 51 be arranged in crank box 22 above, be bearing in simultaneously on this crank box 22.
Be arranged on the camshaft 54 with Aspirating valves 43 and outlet valve 44 corresponding air inlet cams 55 and exhaust cam 56 respectively.Operationally be contained in follower and 55 sliding contacts of this air inlet cam in the cylinder block 23.On the other hand, operating room 58 is formed in cylinder block 23 and the cylinder head 24, and like this, the bottom that enters into this operating room 58 is protruded on the top of follower 57.The bottom that is arranged in the push rod 59 in this operating room 58 is against this follower 57.On the other hand, rocking arm 60 is contained in the cylinder head 24 swingably, and simultaneously its end is against the upper end of Aspirating valves 43, and this Aspirating valves 43 carries out bias voltage by spring along closing direction.The upper end of push rod 59 is against the other end of rocking arm 60.Therefore, push rod 59 along with the rotation of air inlet cam 55 axial operation.Aspirating valves 43 opens and closes by the rocking arm swing that the operation by push rod 59 causes.
Be furnished with between exhaust cam 56 and the outlet valve 44 and air inlet cam 55 and Aspirating valves 43 between mechanism's identical mechanism, like this, outlet valve 44 opens and closes along with the rotation of exhaust cam 56.
Also with reference to figure 4, piston 38, bent axle 27 and eccentric shaft 61 are connected to each other by linkage mechanism 62, and this eccentric shaft 61 is contained in the crank box 22 of engine block 21, are used for moving through cylinder-bore axis C and in perpendicular to the plane of the axis of bent axle 27.
Also with reference to figure 5, auxiliary rod 68 part therebetween has the first semicircle supporting portion 70, half periphery sliding contact of this first semicircle supporting portion 70 and crank pin 65.Be provided with a pair of bifurcated 71 and 72 in the opposite end of auxiliary rod 68, like this, an end of the other end of connecting rod 64 and controlling rod 69 is clipped between bifurcated 71 and 72 with being integral.The second semicircle supporting portion 74 of crank cap 73 and other half periphery sliding contact of crank pin 65.This crank cap 73 is fixed on the auxiliary rod 68.
The other end of connecting rod 64 is connected with an end of auxiliary rod 68 rotationally by cylindrical link pin 75.Pack into auxiliary lever pin 75 in the other end of connecting rod 64 of press fit is rotatably packed in its opposite end and is arranged in the bifurcated 71 of auxiliary rod 68 1 ends.
One end of controlling rod 69 is connected with the other end of auxiliary rod 68 rotationally by cylindrical link pin 76.Link pin 76 passes an end of the controlling rod 69 that inserts the bifurcated 72 that is arranged in auxiliary rod 68 the other ends rotatably.The bifurcated 72 that link pin 76 is packed into and is arranged in the other end in the opposite end Spielpassung.And a pair of clip 77,77 is installed on the bifurcated 72 that is positioned at the other end, and against the opposite end of assisting lever pin 76, throws off so that prevent auxiliary lever pin 76 and this bifurcated 72.
In addition, crank cap 73 is fixed on bifurcated 71 and 72 by the pair of bolts on the opposite side that is arranged in bent axle 27 78.Link pin 75 and auxiliary lever pin 76 are arranged on the extension of axis of bolt 78.
Cylindricality eccentric shaft 61 is integral and is arranged on the running shaft 81 and is in eccentric position, and this running shaft 81 is installed in rotation in the crank box 22 of engine block 21, and has the axis that is parallel to bent axle 27.One end of running shaft 81 is installed in rotation on the side cover 26 of crank box 22 by the ball bearing that is arranged between it and the side cover 26, and the other end is installed on the casing 25 of crank box 22 by the ball bearing that is arranged between it and the casing 25.
Diameter is identical with first actuation gear 51 and can be contained in the relative rotation on the running shaft 81 with second driven gear 85 of these first actuation gear, 51 engagements.Be installed on the running shaft 81 by overrunning clutch 87 with the engagement of second actuation gear 52 and external diameter the 3rd driven gear 86 for the external diameter twice of this second actuation gear 52.This overrunning clutch 87 allows rotary power to pass to running shaft 81 from the 3rd driven gear 86, but makes rotary power not pass to the 3rd driven gear 86 from running shaft 81.
By conversion equipment 88, following state can become another kind of state from a kind of state exchange: power passes to the state of running shaft 81 by second actuation gear 52, the 3rd driven gear 86 and overrunning clutch 87 from bent axle 27, and promptly rotary power passes to the state of running shaft 81 from bent axle 27 with 1/2 reduction speed ratio; And power passes to the state of running shaft 81 by first actuation gear 51 and second driven gear 85 from bent axle 27, and promptly rotary power passes to the state of running shaft 81 from bent axle 27 with constant speed.Conversion equipment 88 is used for according to the following state of engine loading conversion: rotary power passes to the state of running shaft 81 from bent axle 27 with 1/2 reduction speed ratio, provide Higher expansion ratio with convenient engine loading when higher, wherein the stroke of piston 38 in expansion stroke is greater than the stroke in compression stroke; And rotary power passes to the state of running shaft 81 with constant speed from bent axle 27, and constant compression pressure is provided when low with convenient engine loading.
Also with reference to figure 6, conversion equipment 88 comprises: ratchet slider 89, this ratchet slider 89 is endwisely slipping but can not be installed on the running shaft 81 around the counterrotating mode of axis, like this, it selectively with the second and the 3rd driven gear 85 and 86 in an engagement; Shifter 90, this shifter are endwisely slipping but can not be installed on the running shaft 81 around the counterrotating mode of axis; Transmission shaft 91, this transmission shaft 91 can be installed in the running shaft 81 axially slidably, thereby makes the axial motion of shifter 90 pass to ratchet slider 89; Rotatingshaft 92, this rotatingshaft 92 are packed in the casing 25 of crank box 22, are used to wind the rotational perpendicular to running shaft 81; Conversion fork 93, this conversion fork 93 is fixed on the rotatingshaft 92, so that surround shifter 90; And membrane type actuator 94, this membrane type actuator 94 links to each other with rotatingshaft 92.
With reference to figure 7 and 8, ratchet slider 89 is connected with running shaft 81 splines between the second and the 3rd gear 85 and 86.First mesh bulge 95 is arranged on the surface of the ratchet slider 89 that faces toward second driven gear 85 with being integral.Second mesh bulge 96 is arranged on the surface of the ratchet slider 89 that faces toward the 3rd driven gear 86 with being integral.
On the other hand, second driven gear 85 and first lock section 98 are integral, along the rotation of the sense of rotation shown in the arrow 97, this first lock section 98 is used for first mesh bulge, 95 engagements with the ratchet slider 89 that slides to second driven gear 85 by the rotary power that is transmitted by bent axle 27 along with second driven gear 85.The 3rd driven gear 86 and second lock section 99 are integral, along the rotation of the sense of rotation shown in the arrow 97, this second lock section 99 is used for second mesh bulge, 96 engagements with the ratchet slider 89 that slides to the 3rd driven gear 86 by the rotary power that is transmitted by bent axle 27 along with the 3rd driven gear 86.
That is, when ratchet slider 89 slides to second driven gear 85, pass to running shaft 81 with constant speed by first actuation gear 51, second driven gear 85 and ratchet slider 89 from the rotary power of bent axle 27.In this process, the 3rd driven gear 86 is under the effect of overrunning clutch 87 and dally.When ratchet slider 89 slides to the 3rd driven gear 86, slow down with 1/2 reduction speed ratio from the rotary power of bent axle 27, and pass to running shaft 81 by second actuation gear 52, the 3rd driven gear 86 and ratchet slider 89.In this process, 85 idle running of second driven gear.
Shifter 90 is connected with running shaft 81 splines in the position that second driven gear 85 is clipped between this shifter 90 and the ratchet slider 89.Circular groove 100 is arranged around the periphery of shifter 90.
In running shaft 81, be provided with sliding eye 101, its from an end coaxial extension of running shaft 81 to shifter 90 corresponding points.Transmission shaft 91 is slidably mounted in this sliding eye 101.Transmission shaft 91 and shifter 90 are connected to each other by connecting pin 102, and the axis of this connecting pin 102 extends along a radial line of running shaft 81, and like this, transmission shaft 91 axially slides in sliding eye 101 along with endwisely slipping of shifter 90.And, in running shaft 81, be provided with elongated hole 103, be used to make the connecting pin 102 can be with the endwisely slipping and move of shifter 90 and transmission shaft 91, like this, connecting pin 102 passes this elongated hole 103 and inserts.And transmission shaft 91 and ratchet slider 89 are connected to each other by connecting pin 104, and the axis of this connecting pin 104 extends along a radial line of running shaft 81, and like this, ratchet slider 89 endwisely slips along with moving axially of transmission shaft 91.And, in running shaft 81, be provided with elongated hole 105, be used to make the connecting pin 104 can be with the endwisely slipping and move of transmission shaft 91 and ratchet slider 89, like this, connecting pin 104 passes this elongated hole 105 and inserts.
Columnar shaft supporting portion 108 and columnar shaft supporting portion 109 with bottom are arranged on the casing 25 of crank box 22 with being integral, therefore, they with the same axis of the axis normal of running shaft 81 at a certain distance toward each other.The rotatingshaft 92 that one end is arranged in a supporting portion 108 sides is installed in rotation on a supporting portion 108 and 109, and the other end of this rotatingshaft 92 outwards protrudes from axle supporting portion 109.
Below with reference to Fig. 9, actuator 94 comprises: housing 112, and this housing 112 is installed on the support plate 111, and this support plate 111 is fixed on the top of the casing 25 of crank box 22; Film 115, this film 115 is supported in this housing 112, so that the inside of housing 112 is separated into negative pressure chamber 113 and atmospheric pressure chamber 114; Spring 116, this spring are installed under compressive state between this housing 112 and the film 115, so that produce along the spring force of the direction that increases negative pressure chamber's 113 volumes; And actuating rod 117, this actuating rod 117 links to each other with the core of film 115.
The second half housings 119 of the conduit 121 that leads to negative pressure chamber 113 and housing 112 link to each other, and also link to each other with the downstream of air intake passage 46 in the Carburetor 35.That is, the intake negative-pressure in the air intake passage 46 is introduced in the negative pressure chamber 113 in the actuator 94.
The other end of the actuating rod 117 of actuator 94 links to each other with driving arm 122 on being contained in support plate 111, is used for around the rotational that is parallel to rotatingshaft 92.Slave arm 123 is fixed on from the other end of the rotatingshaft 92 of crank box 22 protrusions.Driving arm 122 and slave arm 123 are connected with each other by connecting rod 124.Spring 125 is installed between slave arm 123 and the support plate 111, is used for slave arm 123 is biased into along the clockwise direction of Fig. 9 rotating.
When motor was in low loaded work piece state, at this moment the negative pressure in the negative pressure chamber 113 was higher, and film 115 bendings so that reduce the volume of negative pressure chamber 113 against the spring force of Returnning spring 116 and spring 125, thereby make actuating rod 117 withdrawals, as shown in Figure 9.At this moment, the pivotal position of rotatingshaft 92 and conversion fork 93 is to make first lock section of first mesh bulge 95 of ratchet slider 89 and second driven gear 85 against position engaged.
On the other hand, when motor entered the high capacity working state, at this moment the negative pressure in the negative pressure chamber 113 was lower, film 115 bendings, so that the spring force by Returnning spring 116 and spring 125 increases the volume of negative pressure chamber 113, thereby actuating rod 108 is stretched, as shown in figure 10.Therefore, rotatingshaft 92 and conversion fork 93 turn to second lock section 99 of second mesh bulge 96 that makes ratchet slider 89 and the 3rd driven gear 86 against position engaged.
By rotate conversion fork 93 in the above described manner by actuator 94, in the low loaded work piece process of motor, rotary power from bent axle 27 passes to running shaft 81 with constant speed, and in the high capacity working procedure of motor, reduce with 1/2 reduction speed ratio and pass to running shaft 81 from the rotary power of bent axle 27.
To introduce first embodiment's work below.In the high capacity working procedure of motor, eccentric shaft 61 equal around the rotating speed of the axis of running shaft 81 rotation bent axle 27 rotating speed 1/2.Therefore, when engine loading is higher, 180 degree can be moved by the axis around running shaft 81 in the position of the other end of the controlling rod 69 in the linkage mechanism 62 in expansion stroke and compression stroke, thereby provide Higher expansion ratio, at this moment, the stroke of piston 38 in expansion stroke is greater than the stroke in compression stroke.
On the other hand, in the low loaded work piece process of motor, eccentric shaft 61 equals the rotating speed of bent axle 27 around the rotating speed of the axis rotation of running shaft 81.Therefore, when engine loading was low, the stroke of piston 38 can be constant, and compression ratio can be constant.
When in high capacity when working under the situation, promptly when no matter how engine loading all makes the stroke of piston in expansion stroke greater than the stroke in compression stroke, the decrease of fuel consumption can increase relatively, shown in the dotted line among Figure 11.But, according to the present invention, if compression ratio is constant when engine loading is low, the fuel consumption when engine loading is low can further reduce, shown in solid line among Figure 11.Therefore, when engine loading is low, can further reduce fuel consumption, and when engine loading is higher, also reduce fuel consumption.
Figure 12 to 23 has represented the second embodiment of the present invention.When describing referring to figs 12 to 23 pairs of second embodiment of the present invention, with the part of first embodiment shown in Fig. 1 to 11 or the corresponding part of parts or parts with identical reference number or symbolic representation, and omit detailed description to them.
Referring to figs 12 to 16, the crank box 22 ' of engine block 21 ' comprising: casing 25 ', and this casing 25 ' forms one by casting and cylinder block 23; And side cover 26, this side cover 26 is connected with the opening end of casing 25 '.The 3rd actuation gear 131 is fixedly mounted on the bent axle 27, and in the position near the side cover 26 of crank box 22 ', and the 3rd actuation gear 131 and first driven gear, 53 engagements that are fixed on the camshaft 54.Therefore, pass to camshaft 54 by the 3rd actuation gear 131 that is engaged with each other and first driven gear 53 with 1/2 reduction speed ratio from the rotary power of bent axle 27.
Eccentric shaft 61 ' is arranged on the running shaft 81 with being integral and is in eccentric position, this running shaft 81 is installed in rotation in the crank box 22 ' of engine block 21 ' by the ball bearing 83 and 84 that is arranged between it and the crank box 22 ', and the axis that is parallel to bent axle 27 is arranged.This eccentric shaft 61 ' can pass the other end of controlling rod 69 with the relative rotation.
External diameter is the twice of the 3rd actuation gear 131 and is used for the 4th driven gear 132 with the engagement of the 3rd actuation gear 131 can not counterrotating mode being installed in running shaft 81 '.Therefore, in the working procedure of motor, always pass to running shaft 81 ' with 1/2 reduction speed ratio from the rotary power of bent axle 27.
The supporting center of the other end of the controlling rod 69 in the linkage mechanism 62 can be changed between two states below by conversion equipment 133: promptly, and the state when it departs from the axis (being rotating center) of running shaft 81 ' in the plane perpendicular to the axis of running shaft 81 '; And it and the state of axis (being rotating center) when aliging of running shaft 81 '.Conversion equipment 133 is used for according to engine loading following state being changed: the state when making the rotating center of supporting misalignment running shaft 81 ' of the other end of controlling rod 69, provide Higher expansion ratio with convenient engine loading when higher, at this moment the stroke of piston 38 in expansion stroke is greater than the stroke in compression stroke; And the state of the supporting center that makes the other end of controlling rod 69 when aliging with the rotating center of running shaft 81 ', constant compression pressure is provided when low with convenient engine loading.
Also with reference to Figure 17, conversion equipment 133 comprises: eccentric adjusting sleeve 134, the periphery of this eccentric adjusting sleeve 134 be with respect to eccentric shaft 61 ' off-centre, and surround this eccentric shaft 61 '; Overrunning clutch 139, this overrunning clutch 139 are arranged between this eccentric adjusting sleeve 134 and the eccentric shaft 61 '; Ratchet slider 136, this ratchet slider 136 is contained on the running shaft 81 ', and be used for sliding vertically, and can not rotate relatively around axis, therefore, two some places that it can be chosen in that rotatable phase differs from one another and eccentric adjusting sleeve 134 engagements; Shifter 137, this shifter to be can not counterrotating mode being connected with ratchet slider 136, and surround this eccentric adjusting sleeve 134; Rotatingshaft 92 ', this rotatingshaft 92 ' is installed in the casing 25 ' of crank box 22 ', is used to wind the rotational perpendicular to running shaft 81 '; Conversion fork 138, this conversion fork 138 is fixed on the rotatingshaft 92 ', and is connected with shifter 137; And membrane type actuator 94, this membrane type actuator links to each other with rotatingshaft 92 '.Overrunning clutch 139 is arranged between the other end and eccentric adjusting sleeve 134 of controlling rod 69 of linkage mechanism 62.
When the other end of controlling rod 69 along with piston 38 in cylinder-bore 39 slip and when eccentric adjusting sleeve 134 rotates, overrunning clutch 139 transmits rotatory forces along the direction opposite with the sense of rotation 140 of running shaft 81 ' from controlling rod 69 to eccentric adjusting sleeve 134, but do not transmit rotatory forces to eccentric adjusting sleeve 134, do not transmit rotative powers to eccentric adjusting sleeve 134 yet from running shaft 81 ' along the direction identical from controlling rod 69 with sense of rotation 140.
Eccentric adjusting sleeve 134 has and its all-in-one-piece cylindrical section 134a, this cylindrical section 134a and eccentric shaft 61, and coaxial extension, and stretch to ratchet slider 136.Overrunning clutch 139 is arranged between this cylindrical section 134a and the eccentric shaft 61 '.
Can selectively be applied on the controlling rod 69 according to the work cycle of motor along the load of the direction of compression control bar 69 and along the load of the direction that controlling rod 69 is stretched.When eccentric adjusting sleeve 134 is in that running shaft 81 ' is gone up and when being in eccentric position, also selectively be applied on the controlling rod 69 towards the rotating force of a side and towards the rotating force of opposite side from controlling rod 69.Because overrunning clutch 139 is arranged between eccentric adjusting sleeve 134 and the eccentric shaft 61 ', eccentric adjusting sleeve 134 can only be by the power that applies by controlling rod 69 by rotating along the direction opposite with the sense of rotation 140 of running shaft 81 '.
The 3rd mesh bulge 141 is integrally formed into the place, end in the cylindrical section 134a of the close ratchet slider 136 of eccentric adjusting sleeve 134, so that more circumferentially locating the radially outward protrusion.
On the other hand, ratchet slider 136 is connected with running shaft 81 ' spline between the cylindrical section 134a of eccentric adjusting sleeve 134 and the 4th driven gear 132.Can selectively be arranged on the surface of the ratchet slider 136 relative with cylindrical section 134a with third and fourth lock section 142 and 143 of the 3rd mesh bulge 141 engagements with being integral.
With reference to Figure 18, the 3rd lock section 142 is arranged on the periphery of ratchet slider 136, like this, along sense of rotation 140 rotations, the 3rd lock section 142 and the 3rd mesh bulge 141 mesh by the rotary power that is transmitted by bent axle 27 along with the ratchet slider 136 that slides to the 4th driven gear 132.
The 3rd lock section 142 in the above described manner with the situation of the 3rd mesh bulge 141 engagement under, the center of the rotating center C1 of running shaft 81 ', the center C 2 of eccentric shaft 61 ' and eccentric adjusting sleeve 134 (being the supporting center C 3 of the other end of controlling rod 69) is in relative position shown in Figure 19.When the distance table between the center C 2 of the rotating center C1 of running shaft 84 ' and eccentric shaft 61 ' was shown B, the distance A between the supporting center C 3 of the other end of the rotating center C1 of running shaft 81 ' and controlling rod 69 was arranged to make A=B * 2.
With reference to Figure 20, the 4th lock section 143 is arranged in the interior week of ratchet slider 136, like this, along sense of rotation 140 rotations, the 4th lock section 143 and the 3rd mesh bulge 141 mesh by the rotary power that is transmitted by bent axle 27 along with the ratchet slider 136 that slides to eccentric adjusting sleeve 134.
The 4th lock section 143 in the above described manner with the situation of the 3rd mesh bulge 141 engagement under, the center of the rotating center C1 of running shaft 81 ', the center C 2 of eccentric shaft 61 ' and eccentric adjusting sleeve 134 (being the supporting center C 3 of the other end of controlling rod 69) is in relative position shown in Figure 21, and the supporting center C 3 of the other end of the rotating center C1 of running shaft 81 ' and controlling rod 69 is in same position.That is, third and fourth lock section 142 and 143 is arranged in the positions that rotatable phase on the ratchet slider 136 differs 180 degree each other.
Columnar shaft supporting portion 144 and columnar shaft supporting portion 145 with bottom are arranged on the casing 25 ' of crank box 22 ' with being integral, therefore, they with the same axis of the axis normal of running shaft 81 ' at a certain distance toward each other.The rotatingshaft 92 ' that one end is arranged in a supporting portion 144 sides is installed in rotation on a supporting portion 144 and 145, and the other end of this rotatingshaft 92 ' outwards protrudes from axle supporting portion 145.
Also with reference to Figure 22, the actuating rod 117 of actuator 94 links to each other with driving arm 122, and this driving arm 122 is contained on the support plate 111, is used for around the rotational that is parallel to rotatingshaft 92 '.Slave arm 123 is fixed on from the other end of the rotatingshaft 92 ' of crank box 22 ' protrusion.Driving arm 122 and slave arm 123 are connected with each other by connecting rod 124.Spring 125 is installed between slave arm 123 and the support plate 111, is used for slave arm 123 is biased into along the clockwise direction of Figure 22 rotating.
When motor was in low loaded work piece state, at this moment the negative pressure in the negative pressure chamber was higher, and film 115 bendings so that reduce the volume of negative pressure chamber 113 against the spring force of Returnning spring 116 and spring 125, thereby make actuating rod 117 withdrawals, as shown in figure 22.At this moment, rotatingshaft 92 ' and conversion fork 138 are in and make the pivotal position of ratchet slider 136 near eccentric adjusting sleeve 134, thereby make the 3rd mesh bulge 141 and 143 engagements of the 4th lock section.
On the other hand, when motor entered the high capacity working state, at this moment the negative pressure in the negative pressure chamber 113 was lower, and film 115 bendings so that increase the volume of negative pressure chamber 113 by the spring force of Returnning spring 116 and spring 125, thereby stretch actuating rod 117.Therefore, rotatingshaft 92 ' and conversion fork 138 are in and make the pivotal position of ratchet slider 136 near the 4th driven gear 132, thereby make the 3rd mesh bulge 141 and 142 engagements of the 3rd lock section.
By rotate conversion fork 138 in the above described manner by actuator 94, in the low loaded work piece process of motor, pass to running shaft 81 from the rotary power of bent axle 27 reduction speed ratio under the supporting center C 3 of the other end of controlling rod 69 and state that the axis of running shaft 81 ' (being rotating center C1) aligns with 1/2, and in the high capacity working procedure of motor, depart from the supporting center C 3 of the other end of controlling rod 69 from the rotary power of bent axle 27 that the reduction speed ratio with 1/2 passes to running shaft 81 ' under the state of axis (being rotating center C1) of running shaft 81 '.
To introduce second embodiment's work below.In the high capacity working procedure of motor, depart from the supporting center C 3 of the other end of controlling rod 69 under the state of axis (being rotating center C1) of running shaft 81 ', eccentric shaft 61 ' equal around the rotating speed of the axis rotation of running shaft 81 ' bent axle 27 rotating speed 1/2.Therefore, when engine loading is higher, 180 degree can be moved by the axis around running shaft 81 ' in the position of the other end of the controlling rod 69 in the linkage mechanism 62 in expansion stroke and compression stroke, thereby provide Higher expansion ratio, at this moment, the stroke of piston 38 in expansion stroke is greater than the stroke in compression stroke.
On the other hand, in the low loaded work piece process of motor, under the supporting center C 3 of the other end of controlling rod 69 and state that the axis (being rotating center C1) of running shaft 81 ' aligns, eccentric shaft 61 ' equals the rotating speed of bent axle 27 around the rotating speed of the axis rotation of running shaft 81 '.Therefore, when engine loading was low, this higher compression ratios can be constant.
Like this, when engine loading was low, this motor can be with constant compression pressure work, and when engine loading was higher, this motor can be with Higher expansion ratio work.Therefore, when engine loading is low, can further reduce fuel consumption, when engine loading is higher, also reduce fuel consumption simultaneously.
In a second embodiment, the difference of rotatable phase each other that third and fourth lock section 142 and 143 is arranged on the ratchet slider 136 is the position of 180 degree, but under the low loaded work piece state of motor, rotatable phase difference between third and fourth lock section 142 and 143 can be set to the value less than 180 degree, and assurance simultaneously makes the supporting center C 3 of the other end of controlling rod 69 align with the axis (being rotating center C1) of running shaft 81 '.
Although by the agency of embodiments of the invention, should be known in the present invention and can't help the foregoing description to limit, under the situation that does not break away from the theme of determining by claim of the present invention, can carry out various variations in design.
Claims (1)
1. variable stroke engine comprises: connecting rod, and an end of this connecting rod links to each other with piston by wrist pin; Sub-arm, an end of this sub-arm is connected rotationally with the other end of connecting rod, and this sub-arm links to each other with bent axle by crank pin; And controlling rod, an end of this controlling rod is connected with the position of sub-arm at the link position that leaves connecting rod; The bearing position of the other end of this controlling rod can move in perpendicular to the plane of crankshaft center line,
Wherein, this motor also comprises conversion equipment, and this conversion equipment can changed between the following state: the state of Higher expansion ratio is provided when engine loading is higher, thereby makes the stroke of piston in expansion stroke greater than the stroke in compression stroke; And the state that constant compression pressure is provided when engine loading is low.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP336292/2002 | 2002-11-20 | ||
| JP2002336292 | 2002-11-20 | ||
| JP270282/2003 | 2003-07-02 | ||
| JP2003270282A JP2004183644A (en) | 2002-11-20 | 2003-07-02 | Stroke variable engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1502799A true CN1502799A (en) | 2004-06-09 |
| CN100359145C CN100359145C (en) | 2008-01-02 |
Family
ID=32314102
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101152272A Expired - Fee Related CN100359145C (en) | 2002-11-20 | 2003-11-20 | Stroke changeable engine |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US6814034B2 (en) |
| EP (1) | EP1426585B1 (en) |
| JP (1) | JP2004183644A (en) |
| KR (1) | KR20040044355A (en) |
| CN (1) | CN100359145C (en) |
| AU (1) | AU2003262332B2 (en) |
| CA (1) | CA2449763C (en) |
| DE (1) | DE60320512T2 (en) |
| ES (1) | ES2304493T3 (en) |
| TW (1) | TWI235194B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101446237A (en) * | 2007-11-29 | 2009-06-03 | 现代自动车株式会社 | Variable compression ratio apparatus |
| CN101443538B (en) * | 2006-05-12 | 2010-12-22 | 丰田自动车株式会社 | Method for controlling start timing and mechanical compression ratio of actual compression action |
| CN101052822B (en) * | 2004-11-08 | 2011-02-02 | 本田技研工业株式会社 | Device for removing engine vibration and engine whose stroke characteristic are variable |
| CN102449287A (en) * | 2009-06-01 | 2012-05-09 | 史蒂文·D·阿诺德 | Variable stroke and compression ratio engine |
| CN106662011A (en) * | 2014-08-26 | 2017-05-10 | 日立汽车系统株式会社 | Actuator for link mechanism for internal combustion engine, and method for assembling said actuator |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1811199B1 (en) | 2004-11-08 | 2010-07-14 | HONDA MOTOR CO., Ltd. | Engine with vibration elimination system |
| DE102005020270A1 (en) | 2005-04-30 | 2006-11-09 | Daimlerchrysler Ag | Internal combustion engine with variable compression ratio |
| EP1965051B1 (en) * | 2006-09-12 | 2016-01-06 | Honda Motor Co., Ltd. | Engine assembly with variable stroke characteristics |
| JP2009085187A (en) * | 2007-10-03 | 2009-04-23 | Yamaha Motor Co Ltd | Compression ratio variable engine |
| KR100969376B1 (en) * | 2008-03-31 | 2010-07-09 | 현대자동차주식회사 | Variable compression ratio apparatus |
| JP2009275552A (en) * | 2008-05-13 | 2009-11-26 | Honda Motor Co Ltd | Link type stroke variable engine |
| WO2010107139A1 (en) * | 2009-03-18 | 2010-09-23 | Bong Dae Lee | Method for manufacturing a small gasoline engine with high expansion ratio |
| JP5629603B2 (en) * | 2011-02-23 | 2014-11-26 | 本田技研工業株式会社 | Multi-link variable stroke engine |
| DE102011104531A1 (en) * | 2011-06-18 | 2012-12-20 | Audi Ag | Internal combustion engine |
| JP6384020B2 (en) | 2015-01-26 | 2018-09-05 | 日立オートモティブシステムズ株式会社 | Actuator of link mechanism for internal combustion engine |
| JP6408095B2 (en) * | 2017-09-07 | 2018-10-17 | 日立オートモティブシステムズ株式会社 | Actuator with variable compression ratio mechanism |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1786423A (en) * | 1928-05-07 | 1930-12-30 | Charles P Cady | Internal-combustion engine |
| US4517931A (en) * | 1983-06-30 | 1985-05-21 | Nelson Carl D | Variable stroke engine |
| ATE174661T1 (en) * | 1995-02-28 | 1999-01-15 | Tk Design Ag | COMBUSTION ENGINE OF THE RECIPIENT TYPE WITH VARIABLE COMPRESSION RATIO |
| JPH09228858A (en) | 1996-02-24 | 1997-09-02 | Hondou Jutaku:Kk | Reciprocating engine |
| JP3941371B2 (en) * | 2000-10-12 | 2007-07-04 | 日産自動車株式会社 | Variable compression ratio mechanism of internal combustion engine |
| JP3726678B2 (en) * | 2000-12-15 | 2005-12-14 | 日産自動車株式会社 | Crank mechanism of a multi-link reciprocating internal combustion engine |
-
2003
- 2003-07-02 JP JP2003270282A patent/JP2004183644A/en active Pending
- 2003-11-06 TW TW092131084A patent/TWI235194B/en active
- 2003-11-18 KR KR1020030081491A patent/KR20040044355A/en active Search and Examination
- 2003-11-18 CA CA002449763A patent/CA2449763C/en not_active Expired - Fee Related
- 2003-11-18 AU AU2003262332A patent/AU2003262332B2/en not_active Ceased
- 2003-11-19 US US10/715,829 patent/US6814034B2/en not_active Expired - Fee Related
- 2003-11-20 CN CNB2003101152272A patent/CN100359145C/en not_active Expired - Fee Related
- 2003-11-20 EP EP03257347A patent/EP1426585B1/en not_active Expired - Fee Related
- 2003-11-20 DE DE60320512T patent/DE60320512T2/en not_active Expired - Lifetime
- 2003-11-20 ES ES03257347T patent/ES2304493T3/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101052822B (en) * | 2004-11-08 | 2011-02-02 | 本田技研工业株式会社 | Device for removing engine vibration and engine whose stroke characteristic are variable |
| CN101443538B (en) * | 2006-05-12 | 2010-12-22 | 丰田自动车株式会社 | Method for controlling start timing and mechanical compression ratio of actual compression action |
| CN101446237A (en) * | 2007-11-29 | 2009-06-03 | 现代自动车株式会社 | Variable compression ratio apparatus |
| CN101446237B (en) * | 2007-11-29 | 2013-01-16 | 现代自动车株式会社 | Variable compression ratio apparatus |
| CN102449287A (en) * | 2009-06-01 | 2012-05-09 | 史蒂文·D·阿诺德 | Variable stroke and compression ratio engine |
| CN102449287B (en) * | 2009-06-01 | 2013-11-27 | 史蒂文·D·阿诺德 | Variable stroke and compression ratio engine |
| CN106662011A (en) * | 2014-08-26 | 2017-05-10 | 日立汽车系统株式会社 | Actuator for link mechanism for internal combustion engine, and method for assembling said actuator |
| CN106662011B (en) * | 2014-08-26 | 2019-06-14 | 日立汽车系统株式会社 | The actuator of link lever for internal combustion engine mechanism and the assemble method of the actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| ES2304493T3 (en) | 2008-10-16 |
| TW200415301A (en) | 2004-08-16 |
| US20040149243A1 (en) | 2004-08-05 |
| TWI235194B (en) | 2005-07-01 |
| AU2003262332A1 (en) | 2004-06-10 |
| CA2449763C (en) | 2007-01-02 |
| US6814034B2 (en) | 2004-11-09 |
| DE60320512D1 (en) | 2008-06-05 |
| DE60320512T2 (en) | 2009-06-10 |
| AU2003262332B2 (en) | 2005-02-03 |
| JP2004183644A (en) | 2004-07-02 |
| CN100359145C (en) | 2008-01-02 |
| CA2449763A1 (en) | 2004-05-20 |
| EP1426585A1 (en) | 2004-06-09 |
| EP1426585B1 (en) | 2008-04-23 |
| KR20040044355A (en) | 2004-05-28 |
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